Turbomachine impeller

ABSTRACT

An impeller is provided that may be used in compressors or turbines. In another aspect of the present invention, a fiber or a bundle of fibers is woven to form at least two blades of an impeller. Yet another aspect of the present invention employs a peripheral component woven around impeller blades. An additional conductive fiber or bundle of fibers is woven into the impeller in a further aspect of the present invention. Moreover, an aspect of the present invention provides a chilling system that includes at least one compressor, at least one wave rotor, and a refrigerant.

CROSS REFERENCE TO RELATED APPLICATIONS

This is a divisional application of U.S. patent application Ser. No.11/667,373, filed on May 9, 2007, which is a National Phase ofInternational Application No. PCT/US2005/041085, filed on Nov. 11, 2005,which claims priority to U.S. Provisional patent application Ser. No.60/627,423, filed on Nov. 12, 2004, all of which are incorporated byreference herein.

FIELD OF THE INVENTION

The present invention generally relates to compressors, both apparatusesand methods of use, and more specifically, to compressor impellers.

BACKGROUND

Compressors are machines that increase the pressure of a gas, vapor ormixtures of gases and vapors. The pressure of the fluid is increased byreducing the fluid's specific volume during passage of the fluid throughthe compressor. A cone shaped cylinder with fan blades or an impeller isan integral part in many compressors since it helps with air intake andcompression fluid, as well as directing the flow through the compressor.Depending on the application, impellers may be made of many differentmaterials such as metals or polymers and are typically fabricated byeither casting, molding or machining the material.

The following U.S. patents disclose rotated members with woven fibers:U.S. Pat. No. 3,632,460 entitled “Epicyclic Weaving of Fiber Discs”which issued to Palfreyman et al. on Jan. 4, 1972; U.S. Pat. No.3,718,952, with the same title, which issued to Palfreyman et al. onMar. 6, 1973; U.S. Pat. No. 4,460,531, entitled “Composite FiberReinforced Propeller,” which issued to Harris et al. on Jul. 17, 1984;U.S. Pat. No. 4,255,087, entitled “Member Formed of Fiber-ReinforcedPlastic Material, such as a Rotor Blade,” which issued to Wackerle etal. on Mar. 10, 1981; and U.S. Pat. No. 5,464,325, entitled“Turbo-Compressor Impeller for Coolant,” which issued to Albring et al.on Nov. 7, 1995. All of these patents are incorporated by referenceherein. These prior devices, however, are believed to be prohibitivelyexpensive to produce in volume and do not benefit from inclusion ofmultifunctional component integration. Furthermore, these priorconstructions employ an expensive metal coating, polymeric over-moldingor a composite material, applied after fiber placement, whichconstitutes a greater portion of the part as compared to the fiberportion and is complicated to produce. What is needed is an impellerthat is fabricated by a less expensive method other than casting ormolding.

SUMMARY OF THE INVENTION

In accordance with the present invention, an impeller is provided thatmay be used in compressors or turbines. In another aspect of the presentinvention, a fiber or a bundle of fibers is woven to form at least twoblades of an impeller. Yet another aspect of the present inventionemploys a peripheral component woven around impeller blades. Anadditional conductive fiber or bundle of fibers is woven into theimpeller in a further aspect of the present invention. Moreover, anaspect of the present invention provides a chilling system that includesat least one compressor, at least one wave rotor, and a refrigerant.

The woven impeller of the present invention is advantageous over priordevices since the present invention is less expensive to manufacture, inpart due to material differences, geometric variations and processingsimplicity. The present invention impeller is also advantageous byintegrating components into a multi-functional, single part. Forexample, conductive and/or magnetic fiber members or particle members, ashroud and/or multiple blades, are woven together by the same structuralfiber or bundle of fibers. Also, electric motor integration into theimpeller is employed. Moreover, sharp angles and corners can be achievedwith various embodiments of the present invention. Furthermore, nomolds, prepregs, or post-weaving coatings, moldings or structuralassembly are required. Fluid flow is additionally improved through theweaving patterns and/or hub design. Further advantages and areas ofapplicability of the present invention will become apparent from thefigures, detailed description and claims provided hereinafter. It shouldbe understood that the detailed description and specific examples, whileindicating various embodiments of the invention, are intended forpurposes of illustration only and are not intended to limit the scope ofthe invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will become more fully understood from thedetailed description and the accompanying drawings, wherein:

FIG. 1 is a perspective view showing a first preferred embodiment of awoven impeller of the present invention;

FIG. 2 is a perspective view showing a beginning step of weaving a fiberinto the first preferred embodiment of the woven impeller;

FIG. 3 is a perspective view showing a further step in weaving the fiberinto the first preferred embodiment of the woven impeller;

FIG. 4 is a perspective view showing one completed fiber layer of thefirst preferred embodiment of the woven impeller;

FIG. 5 is a perspective view showing a second preferred embodiment of awoven impeller of the present invention, with an electromagnetic orconductive material;

FIG. 6 is a front elevational view showing the second preferredembodiment of the woven impeller of FIG. 5;

FIG. 7 is a front elevational view showing an alternate embodiment of awoven impeller of the present invention;

FIG. 8 is a perspective view showing a third preferred embodiment of awoven impeller, with an electromagnetic or conductive fiber, of thepresent invention;

FIG. 9 is a front elevational view showing the third preferredembodiment woven impeller of FIG. 8;

FIG. 10 is a diagrammatic side view showing a generic embodiment of thepresent invention;

FIG. 11 is a block diagram showing an alternate, four port wave rotorsystem employed with a condensing wave rotor system of the presentinvention;

FIG. 12 is a block diagram showing a preferred, three port wave rotorsystem employed with a condensing wave rotor system of the presentinvention;

FIG. 13 is a diagrammatic side view showing a first preferred embodimentof the condensing wave rotor system of the present invention,illustrating a woven wave rotor impeller;

FIG. 14 is a diagrammatic side view showing a second preferredembodiment of the condensing wave rotor system of the present invention,illustrating a woven wave rotor impeller;

FIG. 15 is a diagrammatic side view showing a third preferred embodimentof the condensing wave rotor system of the present invention,illustrating a woven wave rotor impeller;

FIG. 16 is a diagrammatic side view showing a fourth preferredembodiment of the condensing wave rotor system of the present invention,illustrating a woven wave rotor impeller;

FIG. 17 is a perspective view showing a fourth preferred embodiment of awoven impeller of the present invention;

FIGS. 18A-18R are diagrammatic top views showing alternate embodimentwoven impellers of the present invention;

FIG. 19 is a diagrammatic, cross-sectional view showing anotheralternate embodiment woven impeller of the present invention, employedwith an electric motor of the condensing wave rotor system;

FIG. 20 is a diagrammatic, cross-sectional view showing anotheralternate embodiment woven impeller of the present invention;

FIG. 21 is a diagrammatic, cross-sectional view of the third preferredembodiment woven impeller of FIGS. 8 and 9;

FIG. 22 is a diagrammatic cross-sectional view showing a furtheralternate embodiment woven impeller of the present invention, employedwith an electric motor of the condensing wave rotor system;

FIGS. 23 and 24 are diagrammatic, cross-sectional views showing fluidflow paths through a series of woven impellers in two variations of thecondensing wave rotor systems of the present invention;

FIGS. 25 and 26 are diagrammatic side views showing preferredembodiments of fiber wetting processing for a woven impeller of thepresent invention;

FIG. 27 is a fragmentary, perspective view showing a fiber windingmachine for a woven impeller of the present invention;

FIG. 28 is a diagrammatic view showing another preferred embodimentcondensing wave rotor system of the present invention; and

FIG. 29 is an exploded, perspective view showing an axial wave rotoremployed in all of the preferred condensing wave rotor systems disclosedherein.

DETAILED DESCRIPTION

The following description of the various embodiments is merely exemplaryin nature and is in no way intended to limit the invention, itsapplication, or uses. The present invention provides a woven impellerand applications of its use.

The present invention provides woven impellers for use in compressorsand more particularly, a condensing wave rotor system. Compressors areused to increase pressure of a wide variety of gases and vapors for amultitude of purposes. A refrigeration compressor is used to compress agas formed in the evaporator. Other applications of compressors includechemical processing, gas transmission, gas turbines, turbochargers, andconstruction. Compressors that accelerate the fluid in a directiongenerally parallel to the rotating shaft consist of pairs of moving andstationary blade rows, each forming a stage. An impeller is a rotatingmember of a turbine, blower, fan, axial or centrifugal pump, or mixingapparatus. An impeller may also be known as a rotor.

Referring to FIG. 1, an impeller 10 is woven from a fiber 12 andincludes eight blade or vane portions 13 and a duct or shroud portion 11which surrounds the blades. Fiber 12 is woven to form blades 13 andshroud 11, and fiber 12 crosses in the center 14 with segments thereofoverlapping each other. The blades and shroud are made as an integral,single piece. FIGS. 2, 3 and 4 show how fiber 12 is woven to createperipheral shroud portion 11 and blade portions 13. Weaving may be doneon a jig designed for such a pattern and woven by hand or preferably theweaving is done on a turn key system such as an automated machine thatis designed to create impeller. The weaving pattern as shown in FIGS. 2,3 and 4 may be altered to create more or less blades or may be alteredto produce the alternative embodiments shown in FIGS. 7 and 18 a-18 q,many of which include a hollow cylindrical center portion 25 (see FIG.7). The alternative embodiment of FIG. 7 has impeller 21 formed by fiber12, and has blade portions 24 and a shroud portion 23. Additional usesfor the alternative embodiment of FIG. 7 include a drive shaft that maybe integrally woven in the area of cylindrical hollow 25 as a singlepiece or a drive shaft that may be attached in such an area 25 to theimpeller.

The preferred embodiment process for woven impeller 10 sequentiallyincludes fiber creation, fiber wetting, fiber winding/weaving andcuring. As can be observed in FIG. 25, a spool 201 containing continuousfiber 12 is automatically fed into a resin bath 203. Resin bath 203 ispreferably a tank containing resin 205 or other coating which will stickto at least the outside of fiber 12. Alternately, resin 205 can besprayed or otherwise deposited onto fiber 12.

An alternate manufacturing process is shown in FIG. 26 wherein a firstmatrix material 207 of pure resin is applied to fiber 12 by way of afirst tank and dispenser assembly 209, and second matrix material 211with ground reinforcing, magnetic or conductive particles, issubsequently or simultaneously applied to fiber 12 via a second tank anddispenser assembly 213. The flow of assemblies 209 and 213 areautomatically actuated by computer (or PLC) controlled valves 215.

More specifically, resin is added in a liquid or gel form prior to orduring the weaving process which is known in the art as “wettingweaving” or “fiber wetting.” The resin is self-hardening so that thewoven impeller hardens over time after weaving and then is removed froma jig 217 in a hardened form. In other embodiments, the resin may be anepoxy type resin such that it has two components which create theadhesion or self-hardening. The resin may be hardened by temperature andthe woven impeller on a jig may be placed in an oven to enhancehardening. Alternately, the resin may be hardened through use ofultraviolet light. It is noteworthy that a mold is not required, therebyreducing capital expense and manufacturing complexity. Fiber 12 may be aprefabricated fiber with a PVC coating or other polymeric coating whichis on the fiber and has any of the properties and hardening techniquesas described above for resins. In any of the above embodiments, theresin, PVC or polymeric material may optionally contain electromagneticor conductive particles and properties. The weaving or layering over jig217 may include pins that are curved to help give a curved shape to ablade or vane of the impeller. In another variation, the fiber(s) iswoven on a hollow and rigid plastic tube 219 with slots and such aplastic tube becomes part of the impeller, and acts as the primaryshroud portion with the fibers acting as the blade portions. Thefiber(s) are secured in the slots and may or may not be severed at thetube to avoid sharp-angle turns. The plastic tube may optionally containmagnetic or electromagnetic properties.

As can be viewed in FIGS. 25 and 27, a fiber placement processautomatically places and winds multiple individual, resin-coated tows orfiber segments 91 onto the jig 93 or a mandrel 94 at high speed, using anumerically controlled, automatically controlled placement head todispense, clamp, cut and restart each tow during placement. Minimum cutlength (the shortest tow length a machine can lay down) is the essentialply-shape determinant. The fiber placement heads 95 are attached to a5-axis gantry or retrofitted to a filament winding machine 97. Machinesare available with dual mandrel stations to increase productivity and atwo spool, five axis filament winding machine would be desirable,especially if a conductive/magnetic fiber is also employed. A WSH-SuperHornet Winder filament winding machine, which can be obtained fromMcClean Anderson Inc., is the preferred existing machine that iscurrently known but it should be appreciated that many other similarmachines can be employed. Advantages of automated fiber placementfabrication include speed, reduced material scrap and labor costs, partsconsolidation and improved part-to-part uniformity.

To achieve desirable properties in composite components, adhesionbetween fiber and matrix should be optimized. Proper adhesion requiresthat sufficient saturation with resin (wetout) at the fiber-matrixinterface is achieved. To ensure good adhesion, attention is given tofiber surface preparation, such as the use of a surface finish orcoupling agent, often termed sizing. Sizing, applied to glass and carbonfilaments immediately after their formation, serves three purposes: asit enhances the fiber/matrix bond, it also eases processing and protectsthe fibers from breakage during processing. Although it accounts foronly 0.25 to 6.0 percent of total fiber weight, sizing is a dynamicforce in fiber reinforcement performance. Sizing chemistry can beoptimized for manufacturing processes such as pultrusion, filamentwinding and weaving.

High-strength fibers used in advanced composites include not onlycarbon, glass and aramid, but high-modulus polyethylene (“PE”), boron,quartz, ceramic, newer fibers such as polyp-phenylene-2,6-benzobisoxazole (“PBO”), hybrid combinations, and thelike. The basic fiber forms for high-performance composite applicationsare bundles of continuous fibers called tow. Carbon fiber tow consistsof thousands of continuous untwisted filaments, with the filament countdesignated by a number followed by “K,” indicating multiplication by1,000 (e.g., 12K indicates a filament count of 12,000).

Carbon fiber is produced from a variety of precursors, includingpolyacrylonitrile (“PAN”), rayon and pitch. The precursor fibers areheated and stretched to create the high-strength fibers. PAN-basedcarbon fibers offer a range of properties, including good-to-excellentstrength—to 1,000 ksi—and high stiffness. Pitch fibers, made frompetroleum or coal tar pitches, have high-to-extremely-high stiffness andlow-to-negative axial CTE. Typical aerospace-grade tow size ranges from1K to 12K. PAN- and pitch-based 12K carbon fibers are available with amoderate (33 to 35 Msi), intermediate (40 to 50 Msi), high (50 to 70Msi) and ultrahigh (70 to 140 Msi) modulus. (Modulus is the mathematicalvalue that describes the stiffness of a material by measuring itsdeflection or change in length under loading.) Heavy tow carbon fibershave filament counts from 48K up to 320K to 35-Msi modulus and 550-ksitensile strength.

Aramid fibers, composed of aromatic polyamide, provide exceptionalimpact resistance and tensile strength. Standard high-performance aramidfiber has a modulus of about 20 Msi and tensile strength ofapproximately 500 ksi. Commercially available high-strength,high-modulus polyethylene fibers are known for being extremely lightweight, as well as for their excellent chemical and moisture resistance,outstanding impact resistance, anti-ballistic properties and lowdielectric constant. However, PE fibers have relatively low resistanceto elongation under sustained loading, and the upper limit of their usetemperature range is about 98° C./210° F. Quartz fibers, while moreexpensive than glass, have lower density, higher strength and higherstiffness than E-glass, and about twice the elongation-to-break, makingthem a good choice where durability is a priority. Quartz fibers alsohave a near-zero CTE; they can maintain their performance propertiesunder continuous exposure to temperatures as high as 1050° C./1920° F.and up to 1250° C./2280° F., for short time periods. Quartz fiberspossess significantly better electromagnetic properties than glass.Ceramic fibers offer high to very high temperature resistance but lowimpact resistance and relatively poor room-temperature properties.

PBO is a relatively new fiber, with modulus and tensile strength almostdouble that of aramid fiber and a decomposition temperature almost 100°C./212° F. higher. It is suitable for high-temperature applications.Basalt fiber is an inexpensive fiber, similar to glass, but whichexhibits better chemical and alkali resistance than glass. Boron fibersare five times as strong and twice as stiff as steel. They are made by achemical vapor-deposition process in which boron vapors are depositedonto a fine tungsten or carbon filament. Boron provides strength,stiffness and is light weight, possessing excellent compressiveproperties and buckling resistance. Fiber hybrids capitalize on the bestproperties of various fiber types, and may reduce raw material costs.Hybrid composites may combine carbon/aramid and carbon/glass fibers.Natural fibers—sisal, hemp, kenaf, flax, jute and coconut are the mostcommon—are derived from the bast or outer stem of certain plants. Theyhave the lowest density of any structural fiber but possess sufficientstiffness and strength for some applications. All of the fibersdiscussed hereinabove can be used with the present invention dependingupon the usage requirements and operating conditions.

In another preferred embodiment, the impeller fiber layers or segmentsare held together by cross-stitching. The cross-stitching may be a fiberthat is similar to the impeller that is woven perpendicular to thevanes. In some of the embodiments, the cross-stitching includes anelectromagnetic or conductive fiber that is different than fiber 12, aswill be further described hereinafter with regard to FIG. 8. The crossweave may be a fiber made of a Nylon engineering grade polymer oranother lightweight and strong material. The impeller may be generallyrigid and in other embodiments, it may be generally non-rigid andflexile or pliable. In embodiments in which the impeller is non-rigid,the woven fiber impeller spins into shape when rotated in a compressorand, when not being rotated, it folds in an umbrella-like manner so thatit does not impede fluid flow therepast. Typically, a non-rigid impelleris cross-stitched as opposed to using a hardening resin material on thefiber for a rigid impeller.

Referring to FIGS. 5 and 6, a second preferred embodiment woven impeller15 includes a magnetic, electromagnetically energizable, or conductivefiber 16 woven into shroud 11. Fiber 16, as shown in FIGS. 5 and 6, isan individual and separate member woven or placed in alternating layersto continuous, nonconductive fiber 12. Fiber 16 is preferably anelongated and continuous fiber which is resin coated. Fiber 12 is wovensuch that it creates blades 13 and peripheral shroud 11. Thus, fibers 12and 16 integrally create blades 13 and shroud 11 as a single piece.Referring to FIGS. 8, 9 and 21, an additional third preferred embodimentof impeller 27 is shown. In this embodiment, impeller 27 has multiple,shorter electromagnetic or conductive fibers 31 generallyperpendicularly woven into fibers 12 of peripheral shroud 11. Impeller27 is formed by weaving fiber 12 thereby creating blades 13, with acenterpoint 14 (coinciding with its rotational axis), and shroud 11 withengaged fibers 31 permanently integrated therein. Fibers 12 and 31 arecoated with a resin 251 by wetting. An alternate embodiment is shown inFIG. 20 wherein an induction wire 253 of copper, steel, aluminum oralloys thereof, surrounds a majority or more of the stacked segmentlayers of nonconductive, carbon fiber 12 at multiple spaced apartlocations of the shroud. A wetted resin coating binds the segments andfibers together.

A fourth preferred embodiment impeller 261 of the present invention,includes one or more continuous nonconductive fibers 263 woven to definesixteen, spaced apart and curved blades 265, flow-through passages 267with flow dividers 269, a hub area 271 and a peripheral should 273 ofcircular-cylindrical shape. In a variation, the shroud can be severed,remove and discarded from the remainder of the impeller. It is desiredto tightly and closely stack the fiber segments upon each other withminimal space between in order to reduce fluid flow between the layeredsegments. Any remaining gaps are filled in by the resin coating from thefiber wetting process. The pitch of each blade is set by slightlyoffsetting the angle or degree of rotation of each fiber layer segmentrelative to the previously placed layer segment from bottom to top.

FIGS. 18A-18R illustrate various alternate embodiment blade patternseach within a shroud 281. A five-point star pattern of blades 283 isshown in FIG. 18A, a six-point star pattern of blades 285 is shown inFIG. 18B, a seven-point star pattern of blades 287 with a largetransversely spaced hub area 289 are illustrated in FIG. 18C, and aseven-point star pattern of blades 291 (of acute outer angles α) with asmall transversely spaced hub area 293 are illustrated in FIG. 18D.Furthermore, FIG. 18E shows an eight-point star pattern of blades 295(of about 90° outer angles α′) with a large transversely spaced hub area297, and FIG. 18F illustrates an eight-point star pattern of blades 299(of about 45° outer angles α″) with an intermediate transversely spacedhub areas 301. A pie-shaped and centrally crossing configuration of sixblades 303 can be observed in FIG. 18G, and a nine-pointed pattern ofblades 305 (of obtuse outer angles α′″) with a large transversely spacedhub area 307 is shown in FIG. 18H. Similarly, FIGS. 18I, 18J, 18N, 18O,18P, 18Q and 18R illustrate star patterned blades 309, 311, 313, 315,317, 319, 321 and 323, respectively, of nine, ten, ten, eleven, eleven,eleven, eleven and nine-points respectively. Variations of pieconfigurations of centrally crossing blades 331 and 335 are shown inFIGS. 18K and 18M, respectively, with ten and eight blades,respectively. The shrouds may remain attached to the blades as a singlepiece or may be cut off after manufacturing. The blades preferably havecurved shapes and rotate about a central axis during operation. Theshapes and patterns of these blades are significant by minimizingundesired fiber layer segment-to-adjacent segment gaps and gaps, and tominimize shroud-to-blade turn fillets (to maximize working blade surfacearea, while maximizing axial fluid-flow through desired impeller areas).Conductive or magnetic fibers and/or resin with such particles areoptionally applied to any of these embodiments.

Advantages of a woven impeller include the ability to perform scalable,automatic, cheap rapid prototyping and/or mass production of highstrength, lightweight turbomachine impellers. Other advantages includeeasy integration of electromagnetic motor bearing elements during themanufacturing process. In addition, active coils may be easily separatedfrom fluid flow. In some embodiments, a drive shaft and componentssealing such a shaft may be eliminated which can also lead tosimplifying the dynamic system. In some embodiments, the impeller mayinclude electromagnetic bearings or aerodynamic bearings which may beused to compensate for manufacturing imbalances. In a preferredembodiment, the woven impeller comprises a fiber that is about 3millimeters thick. In alternate embodiments, the woven impeller iscomprised of fibers that are less than one millimeter thick. In someembodiments, the woven impeller comprises a single continuous fiber andin other embodiments, the woven impeller comprises one continuous fiberand a second continuous fiber that has electromagnetic properties. Thetransverse impeller diameter may range from about one meter or greaterto about a centimeter or less. Various applications of such an impellerinclude a turbomachine, turbocharger, turbochiller, a turbine, acompressor, a pump, a fan, a blower, a jet engine, or any other suchapplication that impellers or other rotatable members are commonly usedin the art.

The condensing wave rotor system of the present invention, whichpreferably employs a woven impeller, is hereinafter described.Mechanical refrigeration is primarily an application of thermodynamicswherein the cooling medium, or refrigerant, goes through a cycle so thatit can be recovered for re-use. Commonly used basic cycles in order ofimportance are vapor compression, absorption, steam jet or steaminjector, and air. Each cycle operates between two pressure levels, andall except the air cycle uses two phase working medium which alternatescyclically between the vapor liquid and the vapor phases.

Water as a refrigerant (R718) is very beneficial because it is natural,absolutely harmless to man and nature, easily available and there are noproblems disposing it after use. Also it allows the use ofhigh-efficient direct heat exchangers since cold water, refrigerant andcooling water all are the same fluid, mostly just water taken from thetap. As a challenge, relatively high pressure ratios are required sincethe cycle works under a coarse vacuum; they are approximately twice ashigh as pressure ratios when using classical refrigerants like R134a orR12. Combined with the thermodynamic properties of water vapor, thishigh pressure ratio requires approximately a two to four times highercircumferential speed of the turbocompressor impeller or wheel, whichcan only be achieved economically by new special high-performanceturbocompressors. However, most air-conditioning applications requiretwo, bulky and complete radial compressor stages with intercooling. Theisentropic efficiencies of the turbocompressors are substantiallylimited by the required high pressure ratios and the efficiency of thepressure recovery of the steady-flow diffusers, which decelerate thehigh speed vapor flow coming from the high-speed compressor impellers.Hence, flow boundary layers cannot withstand such a high pressure riseand tend to separate more easily from the walls and vanes of such steadyflow devices, thereby reducing the compressor efficiency further.

The key component of a R718 turbochiller is the compressor. Water as therefrigerant has some specific features that complicate this applicationin refrigeration plants with turbocompressors. Since the cycle worksunder course vacuum, volumetric cooling capacity of water vapor is verylow and hence huge volume flows have to be compressed with relativelyhigh pressure ratios. As compared with classic refrigerants like R134aor R12, the use of water (R718) as a refrigerant requires approximately200 times higher volume flow and about double the pressure ratio for thesame applications. Due to thermodynamic properties of water vapor, thishigh pressure ratio requires approximately a 2 to 4 times highercompressor tip speed, depending on impeller design, while the speed ofsound is approximately 2.5 times higher by way of comparison. Reynoldsnumbers are about 300 times lower and the specific work transmission perunit mass has to be about 15 times higher. One way to solve thistraditional problem is shown in FIG. 10. A generic turbochiller 30 has achilled water cycle 37, a first compressor 91, a refrigerant cycle 36, asecond compressor 32, and a cooling water cycle 35. Cooling water cycle35 and chilled water cycle 37 are connected via expansion valve 39.Referring to chilled water cycle 37, a heat source 43 heats water whichflows through stream 45 into an evaporator 42. Evaporated water thenenters first compressor 91. Water that is not forced through thecompressor is collected and cycled through pipe 46 back to the heatsource. After the evaporated water enters first compressor 91, it iscompressed and is refrigerated through an intercooler area 41 which thenis forced into second compressor 32 in compressor condenser area 40.Water vapor that condenses in intercooler region 41 is collected into acollection area that is connected to cooler water cycle collection area49. An exemplary water refrigeration system is disclosed in U.S. Pat.No. 6,427,453 entitled “Vapor-Compression Evaporative Air ConditioningSystems and Components” which issued to Holtzapple et al. on Aug. 6,2002, which is incorporated by reference herein. Any of the previouslydisclosed woven impellers of the present invention may be employed bythe compressors 91 and/or 32 in turbochiller 30, even without a waverotor.

A wave rotor offers great potential and advantages for a condensing waverotor system of the present invention in a refrigeration system, sinceit exploits the enormous density differences of gaseous and liquid fluidby the action of centrifugal forces. This greatly supports theseparation of vapor and condensed fluid in the scavenging process andchannel drying before refilling, which addresses a concern in handlingof phase changes occurring in both directions in axial wave rotors.

Utilizing time-depended flow features, wave rotors represent a promisingtechnology for increasing the overall pressure ratio and the efficiencyof the pressure recovery. As discussed above, for the same inlet andoutlet Mach numbers, the pressure gain in time-dependent flow devicescan be much higher than that obtained in steady flow devices. This alsomay allow for a lower total pressure ratio of the compressor impeller,which is usually associated with a higher isentropic efficiency of thecompressor impeller assuming its aerodynamic quality stays the same(e.g., the same polytropic efficiency). This increases the overallefficiency. Furthermore, the combination of this may then also permitthe use of more compact novel axial compressors with less stages andwill further promote the new environmental friendly and energy efficientR718-technology for refrigeration, air-conditioning and heat pumpapplications of capacities <500 kW, which is hardly available today inform of an economical solution.

A wave rotor is a device that utilizes unsteady wave motion to exchangeenergy by direct work action between fluids. A wave rotor consists of anarray of channels on the periphery of a rotor. As the wave rotorrotates, the ends of the channels are periodically ported to high andlow pressure manifolds or ducts which generate and utilize waves in thechannels. These pressure exchanging wave rotors are typically used as atopping unit to enhance the performance of a gas turbine engine. As atopping cycle in a gas turbine engine, the air from the enginecompressor is directed into the wave rotor through a first port. The airflows into the channels of the rotor and is compressed by a series ofcompression or shock waves. This air leaves the wave rotor through asecond port at a higher pressure than when it entered the wave rotor,and passes to a burner or combustor. After being heated in the burner,the gas returns to the wave rotor through a third port, driving a shockinto the air residing in the channels. This gas is trapped within thechannels as the third port closes at a high pressure. When the waverotor rotates around to a fourth port, the gas expands out into therelatively lower static pressure in the fourth port and flows to thehigh-pressure engine turbine. In passing through the wave rotor, the airis first compressed and then expanded, thus, the wave rotor combines ina single device the functions performed by the compressor and turbine ina high spool. By using a wave rotor topping cycle, combustiontemperatures greater than the turbine inlet temperature can be usedsince the gas leaving the combustor is cooled in expansion before beingsent to the turbine. Also, since the rotor is washed alternately by coolinlet air and hot combustion gas, it is self-cooled and obtains a steadystate temperature significantly lower than the combustion temperature.

The basic concept underlying wave rotors is the transfer of energybetween different fluids with shock and expansion waves. By generatingcompression and expansion waves in appropriate geometries, wave machinescan transfer the energy directly between fluids without using mechanicalcomponents such as pistons or vaned impellers. For example, referenceshould be made to: U.S. Pat. No. 5,297,384 to Paxson issued Mar. 29,1994; U.S. Pat. No. 5,267,432 to Paxson issued Dec. 7, 1993; U.S. Pat.No. 5,894,719 to Nalim et al. issued Apr. 20, 1999; U.S. Pat. No.5,916,125 to Snyder issued Jun. 29, 1999; U.S. Pat. No. 6,351,934 toSnyder issued Mar. 5, 2002; U.S. Pat. No. 6,449,939 to Snyder issuedSep. 17, 2002; U.S. Pat. No. 6,526,936 to Nalim issued Mar. 4, 2003; allof which are incorporated by reference herein.

There are several important advantages of wave rotor machines. Theirrotational speed is low compared with conventional turbomachines, whichresults in low material stresses. From a mechanical point of view, theirgeometries can be simpler than those of conventional turbomachines.Therefore, they can be manufactured relatively inexpensive. Also, therotor channels are less prone to erosion damage than the blades ofconventional turbomachines. This is mainly due to the lower velocity ofthe working fluid in the channels, which is about one-third of what istypical within conventional turbomachines. Another important advantageof wave rotors is their self-cooling capabilities. They are naturallycooled by the fresh cold fluid ingested by the rotor. Therefore, appliedto a heat engine, the rotor channels pass through both cool air and hotgas flow in the cycle at least once per rotor revolution. As a result,the rotor material temperature is always maintained between thetemperature of the cool air, which is being compressed and the hot gas,which is being expanded.

The phase change of the fluid inside the wave rotor in a R718refrigeration application is a major difference to the operation of awave rotor in a traditional gas turbine cycle. Additionally, here thelow pressure fluid is at higher temperature than the high pressurefluid. Coming from the compressor impeller at high-speed, the watervapor flows through a vapor collector that guides it to the inlet portat an end plate of the wave rotor. When a channel is opened by theinterplay of end plate and the rotating rotor, the vapor flows into thechannel. Then, if the high pressure cooling water is introduced from theopposite side, it may be injected dynamically short before the vaporinlet port is closed—meaning before the compression shock wavepropagating into the vapor faster than the phase interface reaches thetrailing edge of the vapor inlet port. To assist uniform inflow of thehigh pressure cooling water, the rotor axis may be vertical and thewater may be injected from the bottom. After the vapor is pre-compressedby a primary shock wave and halted, the incoming water may compress thevapor further and fully condense it, depending on what kind of waverotor has been chosen. A pump supplies the high pressure to the coolingliquid. Its energy consumption might be considered negligible, since theliquid is incompressible. The fluid now in its liquid state serves as a“work capacitor” storing the pump work to release it for the vaporscompression during its expansion in the wave rotor channels. Gravity andpump power may also assist the scavenging and charging of the channels.In advanced configurations, the channels may be curved or bent forreasons like supporting or maintaining the rotation of the rotor moreefficiently like the “free running rotor” mentioned above. Due to theunsteady nature of the device, each channel of the wave rotor isperiodically exposed to both hot and cold flow. This can be timed in away that the channel wall temperature stays approximately at the sametemperature like the incoming cooling fluid, supporting desuperheatingand condensation of the vapor.

Two ways of implementing a wave rotor of a condensing wave rotor system401 of the present invention into an R718 cycle are described below. Asshown in FIG. 11, the first implements a 4-port wave rotor working moresimilar to a gas-turbine-topping wave rotor. This still requires anexternal condenser. The second and preferred implementation, as shown inFIG. 12, employs a 3-port condensing wave rotor that eliminates the needof an external condenser, since full condensation occurs inside the waverotor.

The wave rotor is embedded between the compressor and expansion valveparallel to the condenser. FIG. 11 illustrates how this wave rotor 61 isused to top a R718 refrigeration cycle. In the wave rotor channels, thehigh-pressure cooling water leaves through a conduit 56. A pump 65compresses superheated vapor 52 coming out of a compressor 60. Then theadditional compressed vapor 54 travels from wave rotor 61 to a condenser62 where it condenses while rejecting heat to the environment andreturns through a conduit 55 to wave rotor 61 after a pressure boost bypump 65. During the vapor compression in wave rotor 61, the waterpre-expands at 57 and is then further expanded at 58 into the 2-phaseregion by expansion valve 64. After full evaporation, while picking upthe heat in evaporator 63, refrigerant vapor flowing through conduit 51is pre-compressed in compressor 60 and the cycle continues as describedabove. In this configuration, the phase change mainly happens outsidewave rotor 61. Therefore, the vapor mass flows in and out of the waverotor are nearly equal. The same is true for the mass flows of the waterin and out of the wave rotor. However, the water ports are much smallerthan the vapor port. The advantage of using a wave rotor in thisconfiguration can be realized by comparing the thermodynamics cycles ofthe baseline and the wave-rotor-enhanced cycle. Due to the additionalcompression by the wave rotor, condensation happens at a highertemperature without increasing the pressure ratio of the compressor. Itfirst and importantly enables the system to work with a highertemperature difference and secondly results in a similarly highcoefficient of performance (“COP”) like the baseline cycle has for asmaller temperature difference.

FIG. 12 shows the cycle arrangement with a condensing wave rotor in athree port configuration. Concerning the pressure levels, its functionis similar to a pressure-equalizer taking high 76 and low pressure 72streams and equalizes them to a single “medium” pressure stream 73.However, a condensing wave rotor 81 employs a high-pressure 71,low-temperature liquid 72 to compress and condense a low-pressurehigh-temperature gas 73. Thus, in the wave rotor channels, high-pressurelow-temperature water 76 coming out of a pump 85 compresses superheatedvapor 72 coming out of a compressor 80, desuperheats and fully condensesit. At the beginning of the process, when the high-pressurelow-temperature water 76 is exposed to the low-pressure high-temperaturevapor 72, due to sudden pressure drop, all the heat cannot be containedin the water and the heat surplus transforms into latent heat ofvaporization. It is the so called flash evaporation or flashingphenomenon, resulting in a temperature drop of the water. Therefore, aportion of water suddenly vaporizes which causes a shock wave thattravels through the superheated low pressure vapor existing inside thechannel. After the shock wave has additionally pressurized the vaporinside the channel, incoming water compresses the vapor further whiledesuperheating it. When the vapor pressure has reached saturationpressure, the continuing compression by the incoming water causes phasechange (condensation) of the vapor to water while further transfer of(now latent) heat to the incoming water occurs.

At the only outlet port 73 of wave rotor 81, water is scavenged and thenseparated into two streams 74, 75. One goes to an expansion valve 84 andthe other to a heat exchanger 82, where the heat is ejected to theenvironment. A pump 85 provides the pressure level needed at a highpressure inlet 76 of wave rotor 81. After full evaporation, whilepicking up the heat in an evaporator 83, refrigerant vapor 71 isrecompressed in compressor 80 and the cycle continues as describedabove.

Various embodiments of the use of a wave rotor as part of aturbochiller, condensing wave rotor system 401 of the present inventionare illustrated in FIGS. 13, 14, 15 and 16. The turbochiller systemsvary in size and various preferred embodiments are about one meter orless in diameter. Referring to FIG. 13, a chilling system 100 has achilled water cycle 115, a refrigeration cycle 119 and a cooling watercycle 104. Chilled water cycle 115 includes heat source 110, whichdirects heated water 111 to evaporator 116. In some embodiments theheated water 111 enters the evaporator 116 as a jet stream. Water not ina vapor state is collected at the bottom of 116 and is pumped 113 viastream 112 back to heat source 110. Refrigeration cycle 119 includes atleast one compressor impeller and, in some embodiments, may include twocompressor impellers 403 and 405. In such compression systems, a wovenimpeller discussed above may be utilized. Condenser 105 is connected toa three port wave rotor 101 which is in fluid communication with heatejection 106 and is connected through stream 107 and pump 108 to heatrejection 106 and the cooled water re-enters wave rotor 101 throughstream 109.

Referring to FIG. 14, a chilling system 130 has a chilled water cycle145, a refrigeration cycle 149 and a cooling water cycle 134. Chilledwater cycle 145 includes heat source 140, which directs heated water 141to evaporator 146. In some embodiments, the heated water 141 entersevaporator 146 through water nozzles, misters, atomizers or jets and inthese embodiments the evaporator 146 may include multi contact bodycages which enhance droplet separation by gravity. Water not in a vaporstate is collected at the bottom of 146 and is pumped 143 via stream 142back to heat source 140. Refrigeration cycle 149 includes at least onecompressor impeller and, in some embodiments, includes two compressorimpellers 407 and 409. In such compression systems, a woven impellerdiscussed above may be utilized. Condenser 135 is connected to a threeport wave rotor 141 which is in fluid communication with heat rejection136 and is connected through stream 137 and pump 138 to heat ejection136 and the cooled water re-enters wave rotor 131 through stream 139. Inthis version, the wave rotor is internal to and adjacent an end of thechilling system housing as compared to the external mounting in theprior embodiment.

Referring to FIG. 15, a chilling system 150 has a chilled water cycle165, a refrigeration cycle 169 and a cooling water cycle 154. Chilledwater cycle 165 includes heat source 160, which directs heated water 161to evaporator 166. In some embodiments, evaporator 166 includes a multibuckets evaporator system and such system may enhance gravity dropletseparation. Water not in a vapor state is collected at the bottom of 166and is pumped 163 via stream 162 back to heat source 160. Refrigerationcycle 169 includes at least one compressor impeller and, in someembodiments, may include two compressor impellers 411 and 413. In suchcompression systems, a woven impeller discussed above may be utilized.Condenser 155 is connected to a three port wave rotor 151 which is influid communication with heat ejection 156 and is connected throughstream 157 and pump 158 to heat ejection 156 and the cooled waterre-enters wave rotor 151 through stream 159. The wave rotor is centrallymounted with the housing in this embodiment.

Referring to FIG. 16, a chilling system 170 has a chilled water cycle185, a refrigeration cycle 189 and a cooling water cycle 174. Chilledwater cycle 185 includes heat source 180, which directs heated water 181to evaporator 186. In some embodiments, the heated water 141 entersevaporator 186 through water nozzles, misters, atomizers or jets and inthese embodiments the evaporator 186 may include multi contact bodycages which enhance droplet separation by gravity. In other embodiments,evaporator 186 includes a multi buckets evaporator system and suchsystem may enhance gravity droplet separation. Water not in a vaporstate is collected at the bottom of 186 and is pumped 183 via stream 182back to heat source 180. Refrigeration cycle 189 includes at least onecompressor impeller and, in some embodiments, may include two compressorimpellers 415 and 417. In such compression systems, a woven impellerdiscussed above may be utilized. Condenser 175 is connected to a threeport wave rotor 171 which is in fluid communication with heat ejection176 and is connected through stream 177 and pump 178 to heat ejection176 and the cooled water re-enters wave rotor 171 through stream 179.The wave rotor is also central located inside the housing for thisembodiment. The rotational axis 419 of the wave rotor is coaxiallyaligned with that of the compressor impellers.

The compressor area of the condensing wave rotor system 401, exemplifiedby the embodiment of FIG. 15, is further described as follows. Exemplarycompressor impeller 413 is of the woven type shown in FIGS. 5 and 19,having non-conductive fibers 12 alternating with magnetic fibers 16.Impeller 413 includes a shroud and blades which operably rotate about arotational centerline 19. A drive shaft 431 (see FIG. 15) mechanicallyconnects a hub of impeller 413 to wave rotor 151 along centerline 19. Analternate inner contour of the hub may be arcuate as is shown by fiberends 433, for example with impeller 411. Alternately, conductive fibers16 can be replaced by metallic particles in the resin, preferably onlyat the shroud portion, with no conductive material at the bladeportions, to reduce weight. Impeller 413 acts as a rotating rotor in anelectric motor 434 of the present invention system.

A stationary stator 435 of electric motor 434 includes resin coated,carbon fibers 437 or the like, which are tightly stacked together.Copper induction wires 439 are wound around the spool of structuralfibers 437 and attached together by a curing resin matrix material 441.The resin and wires serve as a radial bearing for the impeller. A smallaxial gap is present between the outer periphery of the impeller and theinner surface of the stator. Thus, electric energization of the stator'sinduction wires 439 causes magnetic fibers or wires 16 of impeller 413to levitate impeller 413 in the center of stator 435 while rotating theimpeller within the stationary stator. Of course, the energization andpermanent magnetism can be reversed between the impeller and stator ifdesired.

Furthermore, a hub 453 includes a curved and leading end surface 451 anda tapered, substantially frusto-conical side surface mounted within eachimpeller 411 and 413. These surfaces of hub 453 improve fluid flowcharacteristics through each impeller, especially when both arecoaxially aligned as shown in FIG. 15. Furthermore, the electric motoraspects are essentially outside of the fluid stream, thereby improvingfluid flow properties of the system.

Alternate impeller 461 and stator 463 shapes are shown in FIG. 22, wherethere are matching concave and convex (or diagonal) adjacent surfaces.This works best with no shroud on the final impeller blades 465. Whentwo or more of such impellers are rotated about their coaxial axis 467,the fluid flows through the circumferential gap 469 and is compressed byblades 465, as is illustrated in the variations of FIGS. 23 and 24.

An additional preferred wave rotor system 671 can be observed in FIGS.28 and 29. System 671 includes a tank-like housing 673 having a lengthof less than about 5 meters, and preferably at or less than 4.7 meters,with an outer diameter width of less than or about 2 meters. The lengthof the present invention is about half that of prior water-basedturbochillers. System 671 further includes an axial (or alternately,radial) condensing wave rotor 674, a woven fiber (or alternately, castmetal or molded polymer) impeller 675 in a compressor 679, a waterevaporator 681, a first pump 683, a cooling tower 685, a second pump 687and a heat source/exchanger 689.

The preferred axial wave rotor is illustrated in FIG. 29. Wave rotor 674includes a circular-cylindrical, outer drum 691 containing multiplechannels 692 elongated parallel to a rotational axis 693. Stationary endplates 694 and 696 contain ports 695 and 697, respectively, thatselectively align with some of channels 692 during rotation of waverotor drum 691 and channels 692. Low pressure water vapor enters a vaporcollector 698 and the enlarged port in end plate 694, while highpressure water enters the smaller port in end plate 694. Furthermore,medium pressure water 699 exists port 697 in end plate 696.

A multi-stage, axial, counter-rotating turbocompressor with a wovencomposite impeller is desirable. For example, the counter rotationadvantageously allows for no swirl before and after the impeller stage,which is different from conventional single impeller stages.Furthermore, guide vanes can be eliminated which reduces size, cost andefficiency losses. Moreover, no fixed guide vanes broaden the operatingrange and the invention can achieve a significantly higher pressureratio in a single stage. Axial compressors, have much smaller diametersthan traditional radial or mixed-flow compressors for the same capacity,such that the radius of the present invention can be reduced to 25% thanthat of traditional compressors. Since the volume reduces with thesquare of the radius, the volume can be about 10 times less thanconventional systems and the related unit cost is reduced with thevolume. Multi-stage compressors are also advantageous by achievingadditional pressure ratios with minimal space. Furthermore, it isalternately envisioned that the condenser and compressor of FIG. 19 maybe vertically arranged in an upright orientation to advantageously savefloor space (see for example, FIG. 29). Other variations include: (a) amulti-bucket evaporator having gravity droplet separation at the bottomof the housing with water jet nozzles, in an internal shell, in a middlesection between two oppositely rotating impellers at the top and theevaporator at the bottom, with a curved vapor path to enhance dropletseparation at the top opening, between the shell and housing (similar toFIG. 15 but without the wave rotor); (b) multiple, parallel andelongated contact body cages for gravity droplet separation at thebottom, water nozzle jets immediately above the cages, a pair ofoppositely rotating impellers at the middle of the housing, withstraight upward vapor flow above and below the impellers and a waverotor at the top (similar to FIG. 14); or (c) employing multi-bucketevaporators in any of the other embodiments previously disclosed hereinoptionally with a high suction head for the evaporator and condenserpumps.

The woven composite impellers of the present invention are advantageousin chillers and other compressor systems. The majority of forces seen byconventional impellers are not from the gas passing through the bladesbut from forces acting in its radial direction due to its own inherentmass rotating at high speeds. Thus, a lightweight and strong impellerovercomes this disadvantage. The lightweight nature of the presentinvention impellers reduce safety issues arising from using heavymaterials and reduces the forces inflicted on the impeller bearings. Thepresent invention lightweight materials also reduce the need forextensive balancing. While the preferred fiber materials have beendisclosed for the impeller, it is alternately envisioned that abiodegradable impeller can be created from a biomass matrix such as asoy bean polymer, flax or cotton fiber, for use in some applications.

While many embodiments of woven impellers and condensing wave rotorsystems have been disclosed, other variations fall within the presentinvention. For example, one or more continuous and elongated strands orfilaments are considered to fall within the disclosed term “fiber(s)”.The term “continuous” for a fiber is considered to be at least 5 cm inlength and preferably long enough to constitute at least one entirepattern layer. Furthermore, weaving of one or more fibers has beendisclosed, however, other fiber placement, stacking of layeringtechniques can be used, such as knitting, looping, draping, stitchingand sewing. Additionally, multiple fibers or bundles of threads creatinga fiber can be used as long as each fiber has a length of about 5 cm orlonger in length (preferably much longer) and are placed in the desiredorientations rather than having a chopped and substantially random fiberorientation. It should also be appreciated that conventional impellermanufacturing techniques, such as casting, molding machining or stampingcan be used with certain aspects of the present invention condensingwave rotor system, however, many advantages of the present invention maynot be realized. Alternately, three or more impellers may be coaxiallyaligned and used in the same compressor to generate higher pressureratios. It is further envisioned that two or more radial wave rotors canbe coaxially aligned and used together, preferably rotating at the samespeed, or alternately at different speeds. The examples and otherembodiments described herein are exemplary and are not intended to belimiting in describing the full scope of apparatus, systems,compositions, materials, and methods of this invention. Equivalentchanges, modifications, variations in specific embodiments, apparatus,systems, compositions, materials and methods may be made within thescope of the present invention with substantially similar results. Suchchanges, modifications or variations are not to be regarded as adeparture from the spirit and scope of the invention.

The invention claimed is:
 1. A turbomachine system comprising: a housinghaving inlet and outlet openings; an impeller including multiple blades,the blades including at least one elongated fiber which is continuousbetween at least two of the blades, a fluid-contacting surface of eachof the blades being of substantially the same thickness at itsperipheral and proximal ends as taken along a rotational axis direction;and fluid flowing through the openings in the housing and contactingagainst the blades of the impeller when the impeller rotates inside thehousing.
 2. The system of claim 1, further comprising a shroudsurrounding a periphery of the blades and being an integral, singlepiece with the blades.
 3. The system of claim 1, further comprising anelectrically conductive member attached to and rotating with theimpeller.
 4. The system of claim 1, further comprising a magnetic memberattached to and rotating with the impeller.
 5. The system of claim 1,wherein the fluid is in a liquid phase when it contacts the blades ofthe impeller.
 6. The system of claim 1, wherein the fluid is at leastpart of a refrigerant material.
 7. The system of claim 1, wherein all ofthe blades of the impeller are woven together by the at least oneelongated fiber.
 8. The system of claim 1, further comprising astationary member located adjacent a periphery of the impeller, andsegments of the at least one elongated fiber defining the blades crosseach other.
 9. The system of claim 1, further comprising a resin holdingtogether layers of the at least one elongated fiber of the impeller, theat least one elongated fiber defining a majority of the blades.
 10. Thesystem of claim 1, further comprising a curved and leading hub surface,and a magnetic bearing mounted adjacent the impeller, the curved hubsurface improving fluid flow characteristics of the fluid flowingthrough the impeller, and the magnetic bearing assisting with rotationof the impeller.
 11. The system of claim 1, wherein the at least oneelongated fiber includes a fiber of at least five centimeters in lengththat continuously extends over at least one entire pattern layer of atleast six blades.
 12. A turbomachine system comprising: a housing havinginlet and outlet openings; an impeller including multiple blades, theblades including at least one elongated fiber which is continuousbetween at least two of the blades; and a shroud surrounding a peripheryof the blades and including the at least one elongated fibercontinuously placed on the shroud and the blades; fluid flowing throughthe openings in the housing and contacting against the blades of theimpeller when the impeller rotates inside the housing.
 13. The system ofclaim 12, wherein at least a stream of the fluid flows through a centralopening of the impeller.
 14. A turbomachine system comprising: animpeller including multiple vanes, a peripheral and substantiallycircular shroud, and a central rotational axis, the shroud spanningbetween the vanes and being spaced away from the axis, the vanes andshroud comprising at least one fiber which includes an at least fivecentimeter long fiber that continuously extends within at least two ofthe vanes and an adjacent section of the shroud; and fluid streamingthrough the impeller and contacting against the vanes.
 15. The system ofclaim 14, wherein the fluid is at least partially water.
 16. The systemof claim 14, wherein the vanes have a pattern which provides a centralopening at the axis.
 17. The system of claim 14, wherein the at leastfive centimeter long fiber crosses itself.
 18. The system of claim 14,wherein the shroud surrounds a periphery of the vanes and is integraland a single piece with the blades.
 19. The system of claim 14, furthercomprising an electrically conductive member attached to and rotatingwith the impeller.
 20. The system of claim 14, further comprising anmagnetic member attached to and rotating with the impeller.
 21. Thesystem of claim 14, further comprising a resin holding together layersof the at least one elongated fiber of the impeller, the at least oneelongated fiber defining a majority of the blades.
 22. A turbomachinesystem comprising: an impeller comprising at least six blades and acentral rotational axis, a fiber continuously extending within all ofthe blades and having a pattern which provides a central opening at theaxis, and the impeller includes a coating that secures together stackedlayers of the fiber on the blades; and fluid contacting against theblades when the impeller rotates around the axis and at least a streamof the fluid flowing through the central opening.
 23. The system ofclaim 22, wherein the coating is a resin.
 24. The system of claim 22,further comprising at least a second fiber continuously extending withinall of the blades and having layers thereof secured together by thecoating, the fibers defining a majority of the blades.
 25. The system ofclaim 22, further comprising a shroud surrounding a periphery of theblades and being an integral, single piece with the blades.
 26. Thesystem of claim 22, wherein the fluid is water.
 27. The system of claim22, further comprising an electrically conductive member attached to androtating with the impeller.
 28. The system of claim 22, furthercomprising a magnetic member attached to and rotating with the impeller.29. The system of claim 22, wherein the blades define a star patternwith the fiber crossing itself.
 30. The system of claim 22, furthercomprising a stationary member surrounding the impeller and a bearing,the bearing acting between a periphery of the impeller and thestationary member.
 31. The system of claim 22, further comprising ahousing within which the impeller rotates and the fluid flows through.32. A turbomachine system comprising: an impeller comprising at leastsix blades and a shroud, at least one continuous fiber being stacked inlayers to define the blades and shroud, a coating located on the stackedat least one fiber to fill in gaps between the layers thereof, and theat least one fiber crossing itself; a magnetic member attached to androtating with the shroud; and a liquid stream flowing through theimpeller and contacting against the blades when the impeller rotates.33. The system of claim 32, wherein the at least one fiber includes anaramid material.
 34. The system of claim 32, wherein the at least onefiber includes a quartz material.
 35. The system of claim 32, whereinthe at least one fiber includes a ceramic material.
 36. The system ofclaim 32, wherein the at least one fiber includes a carbon material. 37.The system of claim 32, wherein the at least one fiber includes a PBOmaterial.
 38. The system of claim 32, wherein the at least one fiberincludes a Boron material.
 39. The system of claim 32, wherein the atleast one fiber includes a high-modulus polyethylene material.
 40. Thesystem of claim 32, further comprising a stationary member surroundingthe impeller and a bearing acting between the shroud and the stationarymember.
 41. The system of claim 32, wherein the coating is resin, whichis free of metal, and the at least one fiber and resin define the finalstructure of the impeller.
 42. A method of using an impeller, the methodcomprising: (a) rotating woven vanes about a central axis, at least twoof the vanes including stacked layers of a fiber, the fiber having alength of at least five centimeters; (b) rotating a shroud about thecentral axis, the shroud being attached to and rotating with the vanes;and (c) streaming a fluid through the vanes and internal to the shroudduring steps (a) and (b), and contacting the fluid against radiallyouter portions of the vanes at substantially the same time as radiallyinner portions of the vanes.
 43. The method of claim 42, furthercomprising a non-metallic resin filling in gaps between the stackedlayers of the fiber, and the fiber creating at least part of the shroudwhich peripherally surrounds the vanes.
 44. The method of claim 42,further comprising at least a second fiber defining a portion of thestacked layers of the vanes, wherein the fibers are woven to create anopen central hub area at the axis between the vanes.
 45. The method ofclaim 42, further comprising rotating a magnetic member attached to theshroud when the fluid contacts the vanes.
 46. The method of claim 42,further comprising rotating an electrically conductive member attachedto the shroud when the liquid contacts the vanes.
 47. The method ofclaim 42, further comprising compressing the fluid by rotating theimpeller, and flowing the compressed fluid passed openly accessibleleading and trailing vane edges which are radially elongated.